Heat exchange unit and air-conditioning apparatus including the same
A heat exchange unit includes a housing having an inflow air passage communicating with an air inlet, and an outflow air passage communicating with an air outlet, a first partition plate that partitions an inside of the housing into the inflow air passage and the outflow air passage, a bellmouth disposed around an opening formed in the first partition plate, a centrifugal fan disposed on the first partition plate via the bellmouth, and a heat exchanger disposed on a downstream side of the centrifugal fan in the housing. The air inlet is open at any surface of the housing having the inflow air passage. The air outlet is open at any side surface of the housing having the outflow air passage. The inflow air passage is formed between a fan inlet and a main plate closest to the fan inlet to reach a rear surface. The fan inlet is an air inlet of the centrifugal fan.
Latest MITSUBISHI ELECTRIC CORPORATION Patents:
- USER EQUIPMENT AND PROCESS FOR IMPLEMENTING CONTROL IN SET OF USER EQUIPMENT
- SEMICONDUCTOR DEVICE AND METHOD OF MANUFACTURING SEMICONDUCTOR DEVICE
- PRE-EQUALIZED WAVEFORM GENERATION DEVICE, WAVEFORM COMPRESSION DEVICE, AND PRE-EQUALIZED WAVEFORM GENERATION METHOD
- POWER CONVERSION DEVICE AND CONTROL METHOD FOR POWER CONVERSION DEVICE
- SEMICONDUCTOR DEVICE, METHOD OF MANUFACTURING SEMICONDUCTOR DEVICE, AND POWER CONVERSION DEVICE
The present disclosure relates to a heat exchange unit and an air-conditioning apparatus including the heat exchange unit.
BACKGROUND ARTFor example, Patent Literature 1 discloses an air-conditioning apparatus including a housing having an air inlet and an air outlet, a bellmouth disposed in the housing, a centrifugal fan disposed behind the bellmouth, and heat exchangers disposed around the centrifugal fan. In the air-conditioning apparatus described in Patent Literature 1, air sucked through the air inlet is blown through the air outlet via the bellmouth, the centrifugal fan, and the heat exchangers.
CITATION LIST Patent LiteraturePatent Literature 1: Japanese Unexamined Patent Application Publication No.
2000-356362
SUMMARY OF INVENTION Technical ProblemIf the heat exchangers are disposed around the centrifugal fan as in the air-conditioning apparatus described in Patent Literature 1, air hardly flows into the heat exchanger located away from the air outlet, that is, closer to the center of the housing, and the efficiency of the heat exchanger decreases significantly. Therefore, the efficiency of the heat exchanger is significantly affected by the position where the air outlet is provided. As a result, there is a restriction on the positions where the air inlet and the air outlet are provided. Thus, the housing of the air-conditioning apparatus described in Patent Literature 1 has a low degree of freedom in terms of disposition depending on actual buildings and layouts. Further, the structures of housings of a majority of related-art air-conditioning apparatus are similar to that of the housing of the air-conditioning apparatus described in Patent Literature 1.
The present disclosure has been made in view of the problem described above and an object thereof is to provide a heat exchange unit in which the degree of freedom in terms of disposition is improved and air flowing to a rear side of a centrifugal fan (away from an air outlet) efficiently passes through a heat exchanger, and to provide an air-conditioning apparatus including the heat exchange unit.
Solution to ProblemA heat exchange unit according to an embodiment of the present disclosure includes a housing having an inflow air passage communicating with an air inlet, and an outflow air passage communicating with an air outlet, a first partition plate that partitions an inside of the housing into the inflow air passage and the outflow air passage, a bellmouth disposed around an opening formed in the first partition plate, a centrifugal fan disposed on the first partition plate via the bellmouth, and a heat exchanger disposed on a downstream side of the centrifugal fan in the housing. The air inlet is open at any surface of the housing having the inflow air passage. The air outlet is open at any side surface of the housing having the outflow air passage. The inflow air passage is formed between a fan inlet and a main plate closest to the fan inlet to reach a rear surface. The fan inlet is an air inlet of the centrifugal fan.
Advantageous Effects of InventionIn the heat exchange unit according to the embodiment of the present disclosure, the air inlet can be formed at any surface of the housing having the inflow air passage and the air outlet can be formed at any side surface of the housing having the outflow air passage. Therefore, the degree of freedom in terms of disposition can be improved. Further, the inflow air passage runs from the air inlet of the centrifugal fan along the main plate closest to the air inlet of the centrifugal fan to reach the rear surface. Therefore, a wide space can be secured between the centrifugal fan and the rear surface of the housing. Thus, air blown to the rear side of the centrifugal fan (away from the air outlet) can efficiently pass through the heat exchanger.
Embodiments 1 to 10 of the present disclosure are described below with reference to the drawings. Note that, in the drawings including
The heat source device 1a-1 according to Embodiment 1 is included in an air-conditioning apparatus together with a load-side device. For example, the air-conditioning apparatus is used for heating or cooling a room in a house, building, or apartment house, that is, an air-conditioned space. The air-conditioning apparatus has a refrigerant circuit in which devices mounted on the load-side device and the heat source device 1a-1 are connected by pipes. The air-conditioning apparatus heats or cools the air-conditioned space by causing refrigerant to circulate through the refrigerant circuit.
Note that the air-conditioning apparatus is described in Embodiment 10.
The heat source device 1a-1 is one type of a heat exchange unit including a heat exchanger and is used as an outdoor unit or a heat source unit.
The load-side device is also one type of the heat exchange unit including the heat exchanger and is used as a load-side unit, a use-side unit, or an indoor unit. Note that the load-side device is described in Embodiment 9.
As illustrated in
The housing 5 has an air inlet 7 and an air outlet 10. The air inlet 7 and the air outlet 10 are open so that the inside and outside of the housing 5 communicate with each other. For example, the air inlet 7 is open at the front, rear, side, or bottom of the housing 5. For example, the air outlet 10 is open at the front of the housing 5. That is, the heat source device 1a-1 does not take in and blow air from the bottom or top of the housing 5, but takes in air from one side of the housing 5 and blows air from the front of the housing 5.
The heat exchanger 4 is provided between a downstream part of the centrifugal fan 3 and the air outlet 10.
The centrifugal fan 3 sends air by rotating about its axis. The centrifugal fan 3 is disposed on a partition plate 41 via the bellmouth 40. The centrifugal fan 3 is driven to rotate by the fan motor 13.
The bellmouth 40 is disposed on a suction side of the centrifugal fan 3 and guides air flowing through an inflow air passage 14A to the centrifugal fan 3. The bellmouth 40 has a part that is gradually tapered from its inlet close to the inflow air passage 14A toward the centrifugal fan 3.
The drain pan 8 is provided below the heat exchanger 4.
Further, the housing 5 has the inflow air passage 14A and an outflow air passage 14B defined by the partition plate 41. That is, the housing 5 is provided with the partition plate 41 that partitions the housing 5 into upper and lower parts to define the inflow air passage 14A and the outflow air passage 14B. The partition plate 41 has an opening through which the inflow air passage 14A communicates with the centrifugal fan 3. The bellmouth 40 is disposed around the opening. Note that the partition of the housing 5 into upper and lower parts means that the housing 5 is partitioned into upper and lower parts in the state illustrated in
The partition plate 41 corresponds to a “first partition plate”.
The inflow air passage 14A communicates with the outside of the housing 5 via the air inlet 7 and is a space where air having passed through the air inlet 7 always passes before being sucked into the centrifugal fan 3. As illustrated in
The outflow air passage 14B communicates with the outside of the housing 5 via the air outlet 10 and is a space where air having passed through the centrifugal fan 3 always passes. The outflow air passage 14B is formed at the top in the housing 5 and communicates with the air outlet 10 to guide air blown from the centrifugal fan 3 to the air outlet 10.
By providing the partition plate 41, the housing 5 has a two-stage structure. Thus, the orientation of the air inlet 7 can be changed by simply detaching and attaching a part of the inflow air passage 14A. That is, in the heat source device 1a-1, the orientation of the air inlet 7 can be selected from among the front, the side located at the top in the drawing sheet of
Note that the part of the inflow air passage 14A includes, for example, a metal plate serving as the bottom of the inflow air passage 14A, metal plates serving as the sides of the inflow air passage 14A, and fasteners such as screws for fixing the metal plates. The air outlet 10 can also be formed at any position selected from the front, the side located at the top in the drawing sheet of
In the housing 5 illustrated in
In the housing 5 illustrated in
In the housing 5 illustrated in
Here, focusing on the structure illustrated in
Note that
Further, the opening area of the air inlet 7 is not particularly limited. The air inlet 7 may be an opening formed in a part of the rear surface of the housing 5 or in the entire rear surface of the housing 5. Further, the number of air inlets 7 is not particularly limited.
Here, description is made of a case where airflows are viewed from the top.
In the housing 5 illustrated in
In the housing 5 illustrated in
In the housing 5 illustrated in
Note that each of the air inlet 7 and the air outlet 10 may be used in an open system but, for example, a duct may be connected thereto. Further, the heat source device 1a-1 may be any type of heat source device out of a floor-standing type, a ceiling-suspended type, and a ceiling-concealed type. In the ceiling-concealed type, fan efficiency can be increased and the housing 5 can be reduced in thickness by using the centrifugal fan 3. Note that the open system means that each of the air inlet 7 and the air outlet 10 is open to a space outside the housing 5 without intervention of, for example, a duct.
Next, the heat exchanger 4 is described.
As illustrated in
The plurality of heat transfer tubes 15 are provided side by side and inserted through the plurality of fins 18. The heat transfer tube 15 may be a circular tube or a flat tube.
The plurality of fins 18 are provided side by side at a constant pitch and the plurality of heat transfer tubes 15 are inserted therethrough.
The refrigerant distribution pipe 19 is connected to the plurality of heat transfer tubes 15 and distributes refrigerant to the heat transfer tubes 15.
The refrigerant collection pipe 20 is connected to the plurality of heat transfer tubes 15 and joins streams of refrigerant flowing through the heat transfer tubes 15.
Refrigerant whose pressure is reduced by a pressure reducing device, which is one of the devices of the refrigerant circuit, flows into the refrigerant distribution pipe 19 and is distributed to the plurality of heat transfer tubes 15 by the refrigerant distribution pipe 19. The refrigerant flowing through each of the plurality of heat transfer tubes 15 exchanges heat with air at portions connected to the fins and flows into the refrigerant collection pipe 20. Streams of the refrigerant flowing into the refrigerant collection pipe 20 are joined and flow out through an outlet of the refrigerant collection pipe 20. The refrigerant flowing out of the refrigerant collection pipe 20 is sucked into the compressor 1, which is one of the devices of the refrigerant circuit. The refrigerant sucked into the compressor 1 is compressed and discharged. The refrigerant discharged from the compressor 1 flows into and exchanges heat in a condenser, which is one of the devices of the refrigerant circuit. Then, the pressure is reduced by the pressure reducing device. In this manner, the refrigerant circulates through the refrigerant circuit.
Next, the heat transfer tubes 15 are described.
In the heat exchanger 4 illustrated in
In the heat exchanger 4 illustrated in
Next, modification examples of the heat exchanger 4 are described.
For example, two heat exchange portions of a heat exchanger 4 may be disposed at different inclination angles as illustrated in
By disposing the heat exchanger 4 as illustrated in
Further, one heat exchanger 4 may be inclined as illustrated in
By inclining the heat exchanger 4 as illustrated in
Further, one heat exchanger 4 may be inclined as illustrated in
By inclining the heat exchanger 4 as illustrated in
As illustrated in
Further, the vertical disposition of the heat exchanger 4 means that the heat exchanger 4 is disposed with its air passing surface running in a direction orthogonal to the partition plate 41.
Further, the inclination of the heat exchanger 4 means that the heat exchanger 4 is disposed with its air passing surface running in a direction oblique to the partition plate 41.
Note that
Embodiment 2 of the present disclosure is described below. In Embodiment 2, description overlapping that of Embodiment 1 is omitted and parts identical or corresponding to those in Embodiment 1 are shown by the same reference signs.
Embodiment 1 is directed to the exemplary case where the heat exchanger 4 faces the front surface of the heat source device 1a-1. In Embodiment 2, heat exchangers 4 are disposed around the centrifugal fan 3. Further, in Embodiment 1, the air outlet 10 is formed at a downstream position relative to the heat exchangers 4, that is, at the front surface of the heat source device 1a-1. In Embodiment 2, the air outlet 10 can be formed at any side.
Specifically, the heat exchangers 4 face the rear surface of the heat source device 1a-2, the front surface of the heat source device 1a-2, the first side surface of the heat source device 1a-2, and the second side surface of the heat source device 1a-2. By disposing the heat exchangers 4 around the centrifugal fan 3, the air outlet 10 can be formed on at least one side out of the rear surface of the heat source device 1a-2, the front surface of the heat source device 1a-2, the first side surface of the heat source device 1a-2, and the second side surface of the heat source device 1a-2. Therefore, according to the heat source device 1a-2, the heat exchangers 4 can be mounted with high density and the heat exchange efficiency can be improved.
Further, an experiment and analysis conducted by the inventors demonstrate that it is important to increase the front surface area of the heat exchanger in order that the heat exchanger be efficiently mounted in a thin housing with its height dimension being smallest among the height, width, and depth dimensions of the housing. That is, by increasing the front surface area of the heat exchanger, the resistance of air passing through the heat exchanger can be reduced and the airflow rate when the centrifugal fan 3 is rotated at an arbitrary rotation speed can be increased.
Therefore, by disposing the heat exchangers 4 around the centrifugal fan 3, the heat exchange efficiency can effectively be improved compared with a case where the heat transfer area when heat exchangers are mounted is increased by increasing a pitch of an array of the heat exchangers or disposing the heat exchangers in multiple arrays. Thus, the disposition of the heat exchangers 4 around the centrifugal fan 3 leads to the increase in the front surface area of the heat exchangers 4. Accordingly, the degree of freedom in terms of disposition of the air outlet 10 can be increased and the heat exchange efficiency can be improved effectively.
Here, description is made of a case where airflows are viewed from the top.
Note that
In the housing 5 illustrated in
In the housing 5 illustrated in
In the housing 5 illustrated in
In the housing 5 illustrated in
By disposing the heat exchangers 4 so that the heat exchangers 4 face the four sides of the housing 5 as described above, the air outlet 10 can be disposed at any side and the degree of freedom in terms of disposition of the air outlet 10 can be improved greatly. Further, the air outlet 10 need not essentially be disposed at any one side but air outlets 10 may be disposed at a plurality of sides or all sides as necessary. Further, the air inlet 7 may be provided at a side having the largest area among the four sides that are the front surface, the first side surface, the second side surface, and the rear surface of the housing 5. In this case, the air passage resistance of the air inlet 7 is further reduced.
Here, description is made of a case where airflows are viewed from the side.
As illustrated in
Next, modification examples of the disposition of the heat exchangers 4 are described.
When the heat exchangers 4 are disposed at two sides as illustrated in
When the heat exchangers 4 are disposed at three sides as illustrated in
As described above, the degree of freedom in terms of disposition of the air outlet 10 increases as the number of disposed heat exchangers 4 increases. Note that, when the heat exchangers 4 are disposed at two or three sides, the air passage resistance can be reduced by disposing the heat exchangers 4 at sides where the control box 2 and the compressor 1 are not disposed.
Note that
Embodiment 3 of the present disclosure is described below. In Embodiment 3, the same description as that of Embodiment 1 and Embodiment 2 is omitted and parts identical or corresponding to those in Embodiment 1 and Embodiment 2 are shown by the same reference signs.
Embodiment 1 and Embodiment 2 are directed to the exemplary case where one centrifugal fan 3 is disposed in the housing 5. In Embodiment 3, a plurality of centrifugal fans 3 are disposed in the housing 5.
Even in a case of a housing 5 having a rectangular shape in top view, high performance can be attained by providing a plurality of centrifugal fans 3. In the case of the housing 5 having the rectangular shape in top view as illustrated in
Further, when the plurality of centrifugal fans 3 are provided, it is appropriate that a fan-to-fan partition plate 11 be provided between the centrifugal fans 3. By providing the fan-to-fan partition plate 11, interference between the centrifugal fans 3 can be suppressed.
The fan-to-fan partition plate 11 corresponds to a “third partition plate”. Further, when the housing 5 has the rectangular shape in top view as illustrated in
Note that the rotational directions of the plurality of centrifugal fans 3 are not particularly limited but interference between airflows of the centrifugal fans 3 can be suppressed and energy efficiency can be improved when the centrifugal fans 3 rotate in opposite directions.
When the plurality of centrifugal fans 3 are disposed at the positions illustrated in
Note that
Embodiment 4 of the present disclosure is described below. In Embodiment 4, the same description as that of Embodiment 1 to Embodiment 3 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 3 are shown by the same reference signs.
Note that, in Embodiment 4 including its modification example, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
Further, in Embodiment 4, the heat exchangers 4 are disposed around the first centrifugal fan 3a and the second centrifugal fan 3b at positions where the heat exchangers 4 face the four sides of the housing 5 as illustrated in
In Embodiment 4, a bypass air passage 6 is provided in the housing 5. Specifically, in the heat source device 1a-4, the bypass air passage 6 is formed in the housing 5 by providing a bypass partition plate 9 in the housing 5 as illustrated in
The bypass partition plate 9 corresponds to a “second partition plate”.
Next, a modification example of the disposition of the heat exchangers 4 is described.
Note that the description is made with reference to
Embodiment 5 of the present disclosure is described below. In Embodiment 5, the same description as that of Embodiment 1 to Embodiment 4 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 4 are shown by the same reference signs.
Note that, in Embodiment 5, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
In Embodiment 5, the bypass air passage 6 is provided in the housing 5 and a part of the fan motor 13 provided on the centrifugal fan 3 protrudes into the bypass air passage 6. As described in Embodiment 4, by providing the bypass air passage 6, air easily flows into the heat exchanger 4 disposed at the rear surface away from the air outlet 10. Thus, sufficient air convection occurs in the bypass air passage 6. Therefore, by causing the part of the fan motor 13 to protrude into the bypass air passage 6, the fan motor 13 can be cooled by using the convection of air flowing through the bypass air passage 6. Accordingly, the quality can be improved.
Further, a cooler and a component to be provided together with the cooler can be reduced by providing the convection cooling function. Thus, the structure can be simplified. When the heat exchangers 4 function as a condenser configured to heat air, on the other hand, air can be heated by waste heat of the fan motor 13. Accordingly, the energy efficiency can be improved.
Note that the description is made with reference to
Embodiment 6 of the present disclosure is described below. In Embodiment 6, the same description as that of Embodiment 1 to Embodiment 5 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 5 are shown by the same reference signs.
Note that, in Embodiment 6, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
In Embodiment 6, the heat exchangers 4 are disposed around the first centrifugal fan 3a and the second centrifugal fan 3b at positions where the heat exchangers 4 face the four sides of the housing 5 as illustrated in
Further, in Embodiment 6, the heat exchanger 4 disposed on at least one side, in this case at the front surface, has a horizontally tilted V-shape in cross section among the heat exchangers 4 disposed on at least two sides. The heat exchangers 4 facing the remaining three sides, that is, the rear surface, the first side surface, and the second side surface, has a linear shape in cross section.
Note that, in
That is, the heat exchanger 22 and the heat exchangers 4 are disposed around the centrifugal fan 3 in the housing 5. By disposing the heat exchanger 22 having the horizontally tilted V-shape in cross section on a part of the sides of the housing 5, the heat exchangers 4 can be mounted with high density. That is, even if the housing 5 is thin, the heat exchangers 4 can be mounted with high density and therefore the heat exchange efficiency can be improved. Further, the energy efficiency can be improved.
Note that, also in Embodiment 6, the bypass air passage 6 is provided in the housing 5.
Airflows in the heat exchanger 22 are described.
As illustrated in
Further, when the bypass air passage 6 is provided, the heat exchanger 22 having the V-shape in side view is disposed near the air outlet 10. Thus, the height of the bypass air passage 6 can be reduced.
A modification example of the disposition of the heat exchanger 4 is described.
As illustrated in
By inclining the heat exchanger 23 as illustrated in
As illustrated in
Note that, as illustrated in
Further, the description is made with reference to
Embodiment 7 of the present disclosure is described below. In Embodiment 7, the same description as that of Embodiment 1 to Embodiment 6 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 6 are shown by the same reference signs.
Note that, in Embodiment 7, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
In Embodiment 7, a plurality of centrifugal fans 3 are used and heat exchangers 4 are disposed around each centrifugal fan 3. For example, when two centrifugal fans 3 are used, the heat exchangers 4 are disposed in a shape of eye glasses in top view.
By disposing the heat exchangers 4 around each centrifugal fan 3, the heat exchangers 4 can be mounted with high density. That is, even if the housing 5 is thin, the heat exchangers 4 can be mounted with high density and therefore the heat exchange efficiency can be improved. Further, the energy efficiency can be improved.
Note that description is herein made of an example in which the heat exchangers 4 are disposed around each centrifugal fan 3 in an O-shape in top view but the shape in top view is not limited thereto. Any shape in top view may be employed if the heat exchangers 4 are disposed around each centrifugal fan 3. For example, when the plurality of centrifugal fans 3 are disposed, it is appropriate that the control box 2 be disposed so that its center is located at the center between the centrifugal fans 3. Thus, the ratio between the airflow rates in the respective centrifugal fans 3 that vary due to closure of air passages by the control box 2 can be more balanced among the centrifugal fans 3.
Further, the description is made with reference to
Embodiment 8 of the present disclosure is described below. In Embodiment 8, the same description as that of Embodiment 1 to Embodiment 7 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 7 are shown by the same reference signs.
Note that, in Embodiment 8 including its modification examples, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
As illustrated in
Particularly when the centrifugal fan 3 is mounted in the housing with high density and when the outer periphery of the centrifugal fan 3 is excessively close to the rear surface of the housing 5, the airflow resistance increases abruptly.
Further, the inflow air passage 14A does not reach the front surface of the housing 5 as illustrated in
Further, the heat source device 1a-8 of Embodiment 8 includes a heat exchanger 4 having a horizontally tilted V-shape in cross section. The heat exchanger 4 includes an upper heat exchanger 22a and a lower heat exchanger 22b. As illustrated in
Embodiment 9 of the present disclosure is described below. In Embodiment 9, the same description as that of Embodiment 1 to Embodiment 8 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 8 are shown by the same reference signs.
Note that, in Embodiment 9, it is assumed that the air inlet 7 is formed at the rear surface of the housing 5 and the air outlet 10 is formed at the front surface of the housing 5. However, the positions where the air inlet 7 and the air outlet 10 are formed are not particularly limited.
The load-side device 2a is one type of the heat exchange unit being provided with the heat exchanger and is included in an air-conditioning apparatus together with the heat source device according to any one of Embodiment 1 to Embodiment 8.
Further, the housing layout of the heat source device according to any one of Embodiment 1 to Embodiment 8 is applied to the load-side device 2a. In general, the load-side device 2a may have no compressor 1 or control box 2. That is, the structure of the load-side device 2a is similar to a structure in which the compressor 1 and the control box 2 are omitted from the heat source device according to any one of Embodiment 1 to Embodiment 8.
That is, there is no need to concern the blockage of air passages by the compressor 1 and the control box 2 in the load-side device 2a. Thus, the heat exchangers 4 can be mounted with high density.
Note that
Embodiment 10 of the present disclosure is described below. In Embodiment 10, the same description as that of Embodiment 1 to Embodiment 9 is omitted and parts identical with or corresponding to those in Embodiment 1 to Embodiment 9 are shown by the same reference signs. Note that a refrigerant circuit structure illustrated in
The air-conditioning apparatus 100 includes the compressor 1, a flow switching device 25, the first heat exchanger 4-1, a pressure reducing device 24, and the second heat exchanger 4-2 as main devices. The air-conditioning apparatus 100 includes a first connection pipe 29, a second connection pipe 30, a third connection pipe 31, a fourth connection pipe 26, a fifth connection pipe 27, and a sixth connection pipe 28 as refrigerant pipes connecting the main devices. That is, the air-conditioning apparatus 100 has a refrigerant circuit in which the compressor 1, the flow switching device 25, the first heat exchanger 4-1, the pressure reducing device 24, and the second heat exchanger 4-2 are connected by the refrigerant pipes.
The first connection pipe 29 is a refrigerant pipe connecting the compressor 1 and the flow switching device 25. The second connection pipe 30 is a refrigerant pipe connecting the flow switching device 25 and the first heat exchanger 4-1. The third connection pipe 31 is a refrigerant pipe connecting the first heat exchanger 4-1 and the pressure reducing device 24. The fourth connection pipe 26 is a refrigerant pipe connecting the pressure reducing device 24 and the second heat exchanger 4-2. The fifth connection pipe 27 is a refrigerant pipe connecting the second heat exchanger 4-2 and the flow switching device 25. The sixth connection pipe 28 is a refrigerant pipe connecting the flow switching device 25 and the compressor 1.
The illustration is herein made of the exemplary case where the flow switching device 25 is provided and is capable of switching flows of refrigerant but the flow of refrigerant may be fixed without the flow switching device 25. In this case, the first heat exchanger 4-1 functions only as a condenser and the second heat exchanger 4-2 functions only as an evaporator.
The heat source device 1a-1 is installed in a space other than an air-conditioned space, for example, installed outdoors, and has a function of supplying cooling energy or heating energy to the load-side device 2a.
The load-side device 2a is installed in a space where the cooling energy or the heating energy is supplied to the air-conditioned space, for example, installed indoors, and cools or heats the air-conditioned space by using the cooling energy or the heating energy supplied from the heat source device 1a-1. The description is herein made of the exemplary case where the pressure reducing device 24 is provided in the heat source device 1a-1 but the pressure reducing device 24 may be provided in the load-side device 2a.
The compressor 1 compresses and discharges refrigerant. Examples of the compressor 1 may include a rotary compressor, a scroll compressor, a screw compressor, and a reciprocating compressor. When the first heat exchanger 4-1 functions as a condenser, the refrigerant discharged from the compressor 1 is sent to the first heat exchanger 4-1. When the first heat exchanger 4-1 functions as an evaporator, the refrigerant discharged from the compressor 1 is sent to the second heat exchanger 4-2.
The flow switching device 25 is provided on a discharge side of the compressor 1 and switches flows of refrigerant between the heating operation and the cooling operation. Examples of the flow switching device 25 may include a four-way valve, a combination of three-way valves, and a combination of two-way valves.
The first heat exchanger 4-1 functions as a condenser or an evaporator. Examples thereof may include a fin-and-tube heat exchanger.
The pressure reducing device 24 reduces a pressure of refrigerant passing through the first heat exchanger 4-1 or the second heat exchanger 4-2. Examples of the pressure reducing device 24 may include an electronic expansion valve. Examples of the pressure reducing device 24 may also include a flow resistor obtained by combining a capillary tube and a valve, or the like.
The second heat exchanger 4-2 functions as an evaporator or a condenser. Examples thereof may include a fin-and-tube heat exchanger.
Referring to
In the compressor 1, the refrigerant turns into high-temperature and high-pressure refrigerant superheated vapor and flows into the load-side device 2a through the first connection pipe 29 and the second connection pipe 30. The refrigerant flowing into the load-side device 2a flows into the first heat exchanger 4-1 via the refrigerant distribution pipe 19 and is cooled by exchanging heat with air supplied by the centrifugal fan 3 in the first heat exchanger 4-1. At this time, indoor air passing through the first heat exchanger 4-1 is heated by the refrigerant and is sent to the air-conditioned space such as a living space. Therefore, the air-conditioned space is heated and thus the heating operation is achieved.
The refrigerant cooled by the first heat exchanger 4-1 flows out of the first heat exchanger 4-1 via the refrigerant collection pipe 20 in a state of subcooled liquid or two-phase gas-liquid refrigerant. The refrigerant flowing out of the first heat exchanger 4-1 flows into the pressure reducing device 24 through the third connection pipe 31. In the pressure reducing device 24, the refrigerant is throttled and expanded into a state of low-temperature and low-pressure two-phase gas-liquid refrigerant. The refrigerant flows into the heat source device 1a-1 through the fourth connection pipe 26.
Referring to
In the compressor 1, the refrigerant turns into high-temperature and high-pressure refrigerant superheated vapor and flows into the heat source device 1a-1 through the first connection pipe 29 and the fifth connection pipe 27. The refrigerant flowing into the heat source device 1a-1 flows into the second heat exchanger 4-2 via the refrigerant collection pipe 20 and is cooled by exchanging heat with outdoor air supplied by the centrifugal fan 3 in the second heat exchanger 4-2. The refrigerant cooled by the second heat exchanger 4-2 flows out of the second heat exchanger 4-2 via the refrigerant distribution pipe 19 in a state of subcooled liquid or two-phase gas-liquid refrigerant. The refrigerant flowing out of the second heat exchanger 4-2 flows into the pressure reducing device 24 through the fourth connection pipe 26.
In the pressure reducing device 24, the refrigerant is throttled and expanded into a state of low-temperature and low-pressure two-phase gas-liquid refrigerant. The refrigerant flows into the load-side device 2a through the third connection pipe 31. The refrigerant flowing into the load-side device 2a receives heat from, for example, indoor air. In other words, the indoor air is cooled and the cooling operation is achieved. The refrigerant heated by the first heat exchanger 4-1 turns into two-phase gas-liquid refrigerant or superheated vapor having high quality and is sucked into the compressor 1 through the second connection pipe 30 and the sixth connection pipe 28. The refrigerant sucked into the compressor 1 is compressed again by the compressor 1 and is discharged as high-temperature and high-pressure refrigerant superheated vapor. Thereafter, this cycle is repeated.
Thus, the air-conditioning apparatus 100 includes at least one of the heat source device according to any one of Embodiment 1 to Embodiment 7 and the load-side device 2a according to Embodiment 9. Therefore, the degree of freedom in terms of disposition can be improved greatly.
A modification example of the air-conditioning apparatus 100 is described.
The air-conditioning apparatus 100A includes a gas-liquid separator 34 provided between the pressure reducing device 24 and the second heat exchanger 4-2, a bypass pipe 35 connecting the gas-liquid separator 34 and the outlet of the second heat exchanger 4-2, and at least one flow control device 37 disposed on the bypass pipe 35.
The gas-liquid separator 34 separates refrigerant into gas refrigerant and liquid refrigerant. The gas refrigerant separated by the gas-liquid separator 34 is sent to the flow control device 37. The liquid refrigerant separated by the gas-liquid separator 34 is sent to the second heat exchanger 4-2. The bypass pipe 35 is a refrigerant pipe that guides the gas refrigerant separated by the gas-liquid separator 34 to the outlet of the second heat exchanger 4-2. The flow control device 37 controls the flow rate of the refrigerant flowing through the bypass pipe 35.
The gas-liquid separator 34 is provided on an upstream side of refrigerant during the heating operation relative to the second heat exchanger 4-2 and the opening degree of the flow control device 37 is controlled during the heating operation. Therefore, the refrigerant can be supplied to the refrigerant distribution pipe 19 of the second heat exchanger 4-2 in an optimum refrigerant state depending on an operating condition. Thus, distribution performance is improved. Further, surplus gas refrigerant that does not contribute to heat exchange is bypassed. Therefore, a pressure loss can be reduced in the second heat exchanger 4-2 and the energy efficiency can be improved.
During the cooling operation, the gas-liquid separator 34 functions as a liquid reservoir to exert an effect to reduce a difference in the optimum refrigerant charging amount between the cooling operation and the heating operation. Further, the energy efficiency can be improved by optimizing the refrigerant charging amount.
Embodiments 1 to 8 are described above for the heat source device that is one type of the heat exchange unit according to the present disclosure but some of Embodiments 1 to 8 may be combined. Further, Embodiment 9 is only described for the load-side device that is one type of the heat exchange unit according to the present disclosure but a structure similar to that of a heat source device in any combination of Embodiments 1 to 8 may be applied to the load-side device. Further, Embodiment 10 is only described for the air-conditioning apparatus according to the present disclosure but a heat source device in any combination of Embodiments 1 to 8 and a load-side device in any combination of Embodiments 1 to 8 may be combined arbitrarily. For example, the air-conditioning apparatus 100 may include the heat source device 1a-2 according to Embodiment 2 and a load-side device having a structure similar to that of the heat source device 1a-6 according to Embodiment 6.
Claims
1. A heat exchange unit, comprising:
- a housing having an inflow air passage communicating with an air inlet, and an outflow air passage communicating with an air outlet, with a height dimension of the housing being smallest among the height, width, and depth dimensions of the housing;
- a first partition plate that partitions an inside of the housing into upper parts and lower parts to define the inflow air passage and the outflow air passage;
- a bellmouth disposed around an opening formed in the first partition plate;
- a centrifugal fan disposed on the first partition plate via the bellmouth and causes air to be blown in the circumferential direction in the air passage; and
- a heat exchanger disposed on a downstream side of the centrifugal fan in the housing,
- wherein the housing has two main plates in upper and lower parts of the rotational axis direction of the centrifugal fan and has sides including a front surface, a rear surface, a first side surface and a second side surface in the rotational axis direction of the centrifugal fan;
- wherein the air outlet is open at the front surface;
- wherein the air inlet is open at the rear surface,
- wherein the inflow air passage is formed between a fan inlet and a main plate closest to the fan inlet to reach a rear surface, the fan inlet being an air inlet of the centrifugal fan;
- wherein the heat exchanger has upper and lower heat exchange portions at the front surface;
- wherein the lower heat exchange portion is inclined so that a part closer to the air outlet is located higher than a part closer to the centrifugal fan, and the upper heat exchange portion is inclined so that a part closer to the centrifugal fan is located higher than a part closer to the air outlet;
- wherein the inflow air passage does not reach the front of the housing due to a third partition plate that partitions the inflow air passage and the outflow air passage, and
- wherein the heat exchanger is disposed closer to the air outlet than the third partition plate.
2. The heat exchange unit of claim 1, wherein the housing has a rectangular shape in top view, and the front surface at which the air outlet is formed and the rear surface at which the air inlet is formed are surfaces along a long-side direction of the rectangular shape in top view,
- in the centrifugal fan, a first centrifugal fan and a second centrifugal fan are arranged side by side in a width direction, and
- the heat exchanger is disposed so as to be continuous from the front surface side of the first centrifugal fan and the front surface side of the second centrifugal fan.
3. The heat exchange unit of claim 1, wherein in the centrifugal fan, a first centrifugal fan and a second centrifugal fan are arranged side by side in a width direction, and
- the first centrifugal fan and the second centrifugal fan are disposed so that a central point of the first centrifugal fan and a central point of the second centrifugal fan are located on different straight lines running along the width direction of the housing.
4. The heat-exchange unit of claim 1, wherein the housing has a compressor that compresses refrigerant flowing the heat exchanger, and
- the compressor is arranged closer to a corner of the rear surface side of the housing than the centrifugal fan.
5. The heat exchange unit of claim 1, wherein the upper heat exchange portion and lower heat exchange portion are each inclined away from a plane perpendicular to an axial direction of the centrifugal fan.
6. The heat exchange unit of claim 1, wherein the third partition plate is attached to an end of the first partition plate.
7. The heat exchange unit of claim 1, wherein a fan motor configured to rotate the centrifugal fan is arranged in the outflow air passage.
8. The heat exchange unit of claim 1, wherein the upper heat exchange portion is inclined from a horizontal plane by a first inclination angle, and the lower heat exchange portion is inclined from the horizontal plane by a second inclination angle different from the first inclination angle.
9. The heat exchange unit of claim 1, wherein:
- an axial direction of the centrifugal fan is vertical; and
- the upper heat exchange portion and the lower heat exchange portion are inclined from a horizontal plane.
10. A heat exchange unit comprising:
- a housing having an inflow air passage communicating with an air inlet, and an outflow air passage communicating with an air outlet;
- a first partition plate that partitions an inside of the housing into the inflow air passage and the outflow air passage;
- a bellmouth disposed around an opening formed in the first partition plate;
- a centrifugal fan disposed on the first partition plate via the bellmouth; and
- a heat exchanger disposed on a downstream side of the centrifugal fan in the housing,
- wherein the air inlet is open at a first surface of the housing having the inflow air passage,
- wherein the air outlet is open at a second surface of the housing having the outflow air passage,
- wherein the inflow air passage is formed between a fan inlet and a main plate closest to the fan inlet,
- wherein the heat exchanger is disposed around the centrifugal fan at a position where portions of the heat exchanger face the first surface of the housing and at least one other surface of the housing, and
- wherein the outflow air passage is provided with a second partition plate that defines a bypass air passage that guides, to the air outlet and out of the heat exchanger, air passing through a portion of the heat exchanger that faces the at least one other surface of the housing.
11. The heat exchange unit of claim 10, wherein a part of a fan motor configured to rotate the centrifugal fan protrudes into the bypass air passage.
12. The heat exchange unit of claim 10, wherein the bypass air passage and the housing are formed so that (H3/H1) falls within a range of 10% to 40%,
- where H1 is a height of the housing, and H3 is a height of the bypass air passage.
13. An air-conditioning apparatus, comprising a refrigerant circuit in which a compressor, and a pressure reducing device are connected by pipes,
- wherein the compressor is provided in a heat source device, and
- wherein at least one of the heat source device and a load-side device is the heat exchange unit of claim 10.
14. An air-conditioning apparatus, comprising a refrigerant circuit in which a compressor, a first heat exchanger, a pressure reducing device including an expansion valve, and a second heat exchanger are connected by pipes,
- wherein the first heat exchanger is provided in a load-side device including a heat exchanger unit,
- wherein the compressor and the second heat exchanger are provided in a heat source device, and
- wherein at least one of the heat source device and the load-side device is the heat exchange unit of claim 10.
4449376 | May 22, 1984 | Draper |
4813345 | March 21, 1989 | Kobayashi |
6342005 | January 29, 2002 | Daniels |
6393856 | May 28, 2002 | Gunji |
20070116559 | May 24, 2007 | Higashida |
20100159818 | June 24, 2010 | Sakashita |
20100199697 | August 12, 2010 | Sakashita |
20100287968 | November 18, 2010 | Sakashita |
20130168064 | July 4, 2013 | Akiyoshi |
20130213614 | August 22, 2013 | Ikeda |
20150013376 | January 15, 2015 | Yoshimura |
20150040609 | February 12, 2015 | Yamauchi |
20150071775 | March 12, 2015 | Kashihara |
20150300688 | October 22, 2015 | Yokoyama |
20150316277 | November 5, 2015 | Uemura |
20160076790 | March 17, 2016 | Kojima |
20160138839 | May 19, 2016 | Suhara |
20170089605 | March 30, 2017 | Kim |
20170167737 | June 15, 2017 | Kil |
20180010812 | January 11, 2018 | Moro |
20180209440 | July 26, 2018 | Kono |
20190040873 | February 7, 2019 | Tadokoro |
20190049186 | February 14, 2019 | Yoshimura |
20190101131 | April 4, 2019 | Kono |
20190242612 | August 8, 2019 | Teramoto |
20190316790 | October 17, 2019 | Goto |
20200248924 | August 6, 2020 | Suzuki |
20200284468 | September 10, 2020 | Adachi |
20200309151 | October 1, 2020 | Tanishima |
20210123638 | April 29, 2021 | Yoshioka |
1 775 524 | April 2007 | EP |
2 722 609 | April 2014 | EP |
59-52320 | April 1984 | JP |
2-64824 | May 1990 | JP |
9-145100 | June 1997 | JP |
2000-356362 | December 2000 | JP |
2001-82396 | March 2001 | JP |
2006-29616 | February 2006 | JP |
2006-336909 | December 2006 | JP |
2008-241143 | October 2008 | JP |
2009-24595 | February 2009 | JP |
2016-156512 | September 2016 | JP |
2016-223638 | December 2016 | JP |
2016/158252 | October 2016 | WO |
- International Search Report dated Feb. 12, 2019 in PCT/JP2018/042819 filed Nov. 20, 2018, 2 pages.
- Japanese Office Action dated Jul. 1, 2019 in Japanese Patent Application No. 2019-526337 (with English translation), 11 pages.
- Extended European Search Report dated Nov. 24, 2020 in European Patent Application No. 18889396.0, 11 pages.
Type: Grant
Filed: Nov 20, 2018
Date of Patent: Jan 10, 2023
Patent Publication Number: 20200309407
Assignee: MITSUBISHI ELECTRIC CORPORATION (Tokyo)
Inventors: Yoji Onaka (Chiyoda-ku), Makoto Tanishima (Chiyoda-ku), Takashi Matsumoto (Chiyoda-ku), Takamasa Uemura (Chiyoda-ku), Hiroki Fukuoka (Chiyoda-ku), Rihito Adachi (Chiyoda-ku)
Primary Examiner: Kun Kai Ma
Application Number: 16/763,429
International Classification: F24F 13/30 (20060101);